Measuring and controlling apparatus



June 29, 1948.

Fiied July 17, 1945 c. JOHNSCN ET AL,

' MEASURING AND CONTROLLING APPARATUS 4 Sfieets-Sheef 1 FIG. 2

Ihwentors CLARENCE JOHNSON HARVARD H. 60

RRIE AND "8 PAUL S.D|CKEY attorney June 29, 1948.

C. JOHNSON ET AL MEASURING AND CONTROLLING APPARATUS Filed July 17, 194;

4 Sheets-Sheet 2 FIG. 3

OPE RATING VALVE um I n can POSITIONING VALVE l l ORIIICE Nu.

g 59A v w CLARENCE, JOHNSON,

HARVARD H. sonmamo PAUL s. DICKEY I l/ l 3nnentors June 29, 1948. c, ON ET A; 2,444,101

MEASURING AND CONTROLLING APPARATUS Filed July 17, 1945 4 Sheets-Sheet 3 3nnentors CLARENCE JOHNSON, HARVARD H GORRIE,AND

. u PAUL- S. DICKEY June 29,1948. c. JOHNSON ETAL 2,444,101

MEASURING AND CONTROLLING APPARATUS Filed July 17, 1943 r 4 Sheets-Sheet 4 l I l I I l l I I I I 3m entors CLARENCE JOHNSON, HARVARD H. GORRIE,AND I y PAUL s. DICKEY Patented June 29, 1948 UNITED smrss PATENT OFFICE AND CONTROLLING APPARATUS Clarence J ohnson; South Euclid, -Harvard-H;Gor-

ric, OIeveland-Heights, and Paul S. Dickey, :East Cleveland, Ohio, .assignors to Bailey Meter Gompany, .a corporation of Delaware 1ip1ilicaltioh J-lily 137, 1943, Serial No. 4951088 eating, recording or integrating 'JJhfiE flu'id rate :of

A given orifice 'aI-ea or .ipercentagei-restriction to the fluid how has certain ficwcapacity and pressure differential relations. A rate of tflowmeter for'fluid is usually so :desi-gned;as :to-.-reach amaximum :at a definite value of applied ldilierential pressure, said difierential pressurebeingproduced bythe flow of acertain volume of'fiuidatnefinite density conditions :past .the orifice .-in ;a unit of time. i A quadratic :relation exists between xiii- .ferential pressure and rateof flow so that at .low rates of flow only relatively minute differential pressuresareavailable to actuate a flowlmeter or to .be "visually read :on a manometer, audio-ac- .ouracies of metering mayresult. Should-the rate I of flow for a relatively large portions-of the time -be.a small percentage of the ultimate .maxirnum then it :is desirable to change the rate of howpressure difierential relation for said time .by causing .the given rate of flow toproduceagreater difierential pressure, and thus read at .a higher point on the scale .or graduation. Conversely, should the flow .for certain periods of time .be reater than that necessary to produce .a maximumtpressure:difierentialto whichthe fiow meter will respond, it is desirable to cause .fthegiventrate of flow .to produce alesser differential ,"pressure and thus bring the readings within {the range desired.

lf an extremely .wide range of flowlrate is 'toLbe metered, then it is desirable to break .the .range into anum'berof 'bandsso that equal accuracy .of

. reading orof measurement .maylbe'had lover different portions of the total. "For .eXaml5Ie,.a desired range in flow rate might 'besplit .into ten bands each covering a range .of'10'% of the total. A single manometer or new meter could be used for all of the ten bands .o'ffioW rate if each such band ornow' rate were able .to produce the same range or diiierentialliressures. One way of ac- 15 Claims. (Cl. 138-37) complishing this deslderatum would be to" open the conduit :and change the .orifice plate when it were desired to operate inanother ofrthe bands .of flow rate. This is on the premise that ten rates-of the'example.

The principal'ob-ject of'cur present invention is the necessary-arrangementeand-apparatus where- .by the orificeopening may'be readilyvaried-without the necessity of interfering withithe flowing fluid to change from one lorifice aplate to another. This is accomplished by providing an adjustable orifice plate positionable to provide definite predetermined :flow capacity or differential pressure values.

A iurther object is to rprovidewsuch an adiustable orifice with means for varying the orifice area accuratelyand speedily from a remote point.

With these and further objects in view we will now describe the embodiments of our'invention which we have illustrated.

In the drawing:

Fig. 1 is an elevation, partially r-in section, .of a preferredembodiment .of our invention, including in somewhat diagrammatic :fashion interconnections with remote control stations.

Fig. 2 is aschematic.showingof oneof the remote control stations.

Fig. .3 is an elevation, partially in section, of -a modification. of'our invention.

.Fig. 4 is a sectional detail, to larger scale, .of a pneumatic stop of Fig. 3.

Fig, 5 .isa view-of Fig. .4in thedirection of the arrows 55.

Fig. 6 is .a diagrammatic layout .of thepn-eumatic control system ofFig. 3.

Fig. '7 isa diagrammatic layout ofapneumatic control system similar .to .that of .Fig. .6 but adapted for a larger number .of positions.

Referring now tofE'ig. 1,, Weshowthereinahody member I adapted to .form apart of a conduit through which .afiu'id to be measured is flowing andhaving a bore 2 of a .diametercoinciding with the opening in the conduit. Frequently .it is .desirable to eguipthe member .I witha liner .3 of corrosion resistant material so that the area of the bore '2 adjacent the orifice plate 4 is substantially invariable. fTheportion of the 'bore 2. which .is obstructed .by the orifice plate 4 .determines the pressure differential acrosssaidorifice plate for any given rate of how. Inasmuch as accuracy of measurement depends upon the exactness to which the orifice plate 4 ispositione-d relative to the bore 2,, theprinci'pal object of our invention is the provision of means .through either of the two positions.

Movable "adjacent the member 8 is a member 9 pivoted as at H) to the housing H. The housin |I surrounds and protects the piston rod 1 and member 8. besides providing a bearing for the pivot l3. The housing may be slotted to allow free movement of the member 3 and of its driving arm l2. For moving the member 3 we provide a power cylinder l3 having a piston M and piston rod E5, the latter pivotally connected to the arm I2 through a link l6.

For remote positioning of the orifice plate 4 we provide a transfer valve l1 and a selector valve l8. The transfer valve I! has two operating positions, namely, that of Fig. 1 and that of Fig. 2, diagrammatically shown with the handle I9 adapted to move the blocking portion 2|] to In the position shown inFig. Lwhich we term a normal position,"air under substantial pressure is available at the pipe 2|,-'th1'ough the transfer valve I! and the pipe 22, to the'cylinder 5 above the piston'B tending to urge the piston 6 in a. downward direction. At the same time the pipe 23, which connects with the cylinder 5 below the iston 6, exhaust through the transfer valve H to the atmosphere. Thus, in the position shown, the piston 6 is urged in a downwardly direction by full air pressure on'its top and with that portion of the cylinder which is below the piston 6 open to the atmosphere. With the transfer valve H in its reset position, as shown'in Fig. 2, the reverse condition exists, namely, that fluid pressure from the supply line 2| is effective below the piston 65, while the other end of the cylinder 5 is exhausted to'the atmosphere through the pipe 24, and the piston is urged upwardly.

Th selector valve manual relay whereby we are enabled to establish fluid loading pressures each equivalent to, or representative of, one of the preselected positions of the orifice plate 4, or specifically one of the steps on the member 3. In other words, the

selector valve l8 positions the member 9 to the selected step to which the piston rod 1 is to be moved. 7

The drive mechanism i3, M consists of a double-acting air cylinder provided with a bellows-actuated double acting air pilot valve and restoring spring which causes the piston M to assume a definite position for every incoming air control pressure. Thus the bellows receives an .airloading pressure through the pipe 26 from the selector valve Hi and positions the pilot valve '21 to a definite position corresponding thereto. The movable end of the bellows 25 is connected by means of a yoke to one end of a loading spring '28, the other end of which is positioned by and with the piston rod l5. Air pressures from the pilot valve 21 are admitted through the pipes 23 and to opposite sides of the piston M. V I

From a position of rest an increase in air load .ing pressurethrough the pipe 26 causes the upper end of the bellows 25 to move upwardly, thus l8 constitutes a remote extending the spring 28 and positioning the pilot valve 21 upwardly. Such upward positioning of the pilot 27 tends to increase the air pressure effective through the pipe 30 above the piston l4 and decrease the air pressure acting through the pipe29 below the piston Hi. This results in a downward positioning of the piston 14 with resultant downward pull on the loading spring 23 acting against the movable head of the bellows 25. The force applied by the spring upon the bellows is then proportional to drive position, If

and when it is equal to that due to the incoming control air pressure within the bellow 25 the double acting pilot valve 21 is in neutral, the air pressures applied to th piston M are in balance and no further movement of the piston It takes place. Thus for each and every loading pressure applied to the bellows 25 there is a corresponding definite position of the piston l4 and of the member 9.

For establishing within the bellows 25 loading pressures corresponding to the various steps or lands of the member 9 we provide the selector valve mechanism l3 with a hand knob 3| arranged to load or unload a spring 32 and bellows 33. Fastened to the movable end of the bellows 33 and to one side of the loading spring 32 is a valve actuator 34 arranged to either admit air to the chamber 35 or to cause a discharge of air from the chamber to the atmosphere. The knob 3| is on a stem screw threaded through the block 34A into a free block which. presses directly against one side of the spring 32, as shown in Fig. 1. Thus by turning the knob 3| in one direction or the other it moves toward the right or the left and thus tends to compress or release the .compression of the spring 32 against the bellows 33. When the knob 3| is turned in the proper direction to compress the spring 32 and thereby load it, the resultant motion moves the beam 343 to open the inlet valve 340 and close the outlet valve 34D whereby pressure is allowed to build up in the chamber 35.. Increased pressure in the chamber 35, acting within the bellows 33, causes the movable head thereof to be positioned toward the right on the drawing, carrying with it the valve actuator 34 and providing a force opposing the force of the spring 32. A condition of equilibrium is established wherein the pressure within the chamber 35 is directly related to the amount of movement of the knob 3| or of the position thereof relative to a graduated scale or dial. Thus an operator may turn the knob 3| until its pointer indicates a preselected number, as for example the number 6, which establishes a loading pressure within the chamber 35 of a preselected value resulting in a positioning of the piston I4 and thereby of the member 9 until the step or land 6 of the member is in position to limit the downward movement of the piston 6 and piston rod. 1.

In general, the operation is as follows: assume the mechanism positions of Fig. 1. If air pressure is available at the pipe 2| it acts upon the top of piston 6,foroing the piston rod 1, member 8 and orifice plate 4 downwardly until the projection 36 on the member 8 engages land number 6 of the member 9. Inasmuch as the pipe 23 is open to the atmosphere through the connection 24 atmospheric pressure exists below the piston 6 and the piston will be forced downward until conditions are changed.

Assume now that it is desired tovary the orifice opening to a value represented by the step '7 on the member 9. The operator first moves the lnob o'f the transfer valve I'I fromthe-normalposition of Fig. 1 to'the reset position'ofFig. 2 whereby the upper end of cylinder is bledto atmosphere through pipes 22 and 24, while full air pressure from the supply pipe 2| is trans mitted'through the pipe23- to the lower portion This loads the spring 32, increases the loading pressure'within the pipe ZS-and bellows 25, causing an" upward positioning of the pilot 21' and an extension of thesprin 28. Such upward movement of the pilot 2! results in an increase in pressure" through the pipe 39 above the piston I4 and a decrease in pressure through the pipe 29 below the piston I4. This results in a downward movement of the piston I 4, a loading ofthespring 28to counterbalance the increased pressure within the bellows and a return of thepilot 2! to neutralqposition. At the same time the downward movement'of the piston rod I5 has resulted in a clockwise positioning of the member 9 around its. pivot I9, and the arrangement is such that thelpilot 21 reaches its neutral position at ex actly the time that the member land number 7 is in the axial line of member 3. The pilot 2I having reached its neutral position the loading pressures eifective through the pipes 29 and 39 are equal, stopping travel of the piston I4, and the land.7 remains in line with the member 8.

The transfer valve I! is then turned. to its normal position (see Fig. 1) wherein full pressure is eifective above the piston 6, causing the piston to move downwardly until the projection 330i the member 8 engages the land number '7' and .ish'eld in such engagement so long as full pressure is applied above the piston 6 and the cylinder 5 below the pistonfi is exhausted to. the atmosphere.

If'it is desired to move the orifice plate 4170 any position corresponding to a land on the member 9 it is in general only necessary, first, to retract the piston 6. and the member. 8 to their uppermost extent of travel. Second, to position the member 9, through the agency of the selector valve I8, until the desired member land is locatedin line of the member 8.; and third, to

In general} the arrangement of' Fig. 3: provides that the orificeplate' 4 may bepositionedthrougn the agency of the piston 6 in a downwardlydirection until the shoulder 42 on the piston rod' I engages the first oneof the stops 4|, 49; 39 or 38 which it finds in an extended position. In Fig. 4 we indicate that a housing 43 has slidable therein a plunger 44 adapted to be extended toward theleft (on the drawing) through the agency of 'a bellows 45 acting against a loading spring 49 when pressure is applied to the interior of the bellows housing 41 through a pipe connection- 482 When pressure within the pipe 48 cause the member 8V to move downwardly until its projection 36. engages the selected land and is held'insuch engagement which corresponds to, the orifice plate 4 being in the selectedposition.

In Fig. 3 we show another embodiment of our invention. Herein the body member I has been shown at to the showing ofFig. l-so as to more clearly indicate the segment 31 of the bore 2 which is blocked off by the orifice plate 4 in one of its preselected positions. A piston 6, having a piston rod I, is positionable in a power cylinder. 5 for moving and" holdingrthe orifice plate 41 Theorificeplate 4 has four preselected positions as determinedbythe stops 38, 39, 49 and 4|. Fig. 4 is a sectional elevation of one of the stops 39, 49, Or II, and Fig. 5 is a view of Fig, 4. looking in the direction of the arrows 5-5. The stop 38 differsfrom the stops 39, 49and 4|. in that'it is a permanently located stop of minimum travel .of the piston rod I'anddoes not have the: extendible retractible' mechanism of thestops 39; 40and' 4'1.

is released then the spring 46 overcomesthe bollows 45 and retracts the plunger 44 to the position shown in Fig. 4.

In Fig. 5 we indicate that the plunger 44 is eccentric within the housing 43'and that the entire assembly is held against the upright MA by the clamping action-of an encircling plate 49 having a plurality of bolt holes 59 through which are applied'the necessary bolts iii. The purpose of this arrangement is of course so that slight adjustment of vertical location of the stop plunger 44 may be" had by loosening the bolts 5i and slightly rotating the assembly including the eccentrically bored housing 43, thus slightly raising or lowering the plunger 44; and correspondingly slightly varying the area of the segment 3! when the shoulder 42 engages the end of the plunger 44.

In this arrangement we provide a transfer valve HA and. a selector valve IBA somewhat similar to those indicated in-Fi'gs. 1 and 2. The selector valve ISA consists of a series of cam-operated shutofi'valves 58 (Fig. 6), each of which is connected to one of the stop assemblies 39, 49 or M. The cams 56 operating these valves are in turn rotated on a common shaft by the knob'52 relative to numeralsindicating the four stops.

The transfer valve HA is similar to that described in connection with Figs. land 2. The valves HA and ISA are interlocked one withthe other so that it is impossible to operate the knob 52 of the selector valve I8A until the orifice plate 4 is fully retracted toits uppermost position (on the drawing) in the orifice body. This is accomplished as follows: An interlock valve 53 is attached to the orifice upright or superstructure EIA in such a way as to remain closed until th'e orifice plate is fully retracted. At this point the valve arm 54 is positioned under the shoulder 42 of the piston rod I, and the arm 54- (through the forceof spring 11) in turn pushes down the interlock valve stem and opens the valve 53 (Fig. 6), This interlock valve 53 is connected to the bellows I5 of the interlock mechanism in the selector valve I 8A. As the airpressure is thus impressed upon the bellows I5 of this interlock mechanism the stem I6 attached to it moves longitudinally, th'u's disengaging from a lockwheel 51 on the cam shaft. With this wheelunlocked the knob 52 can be turned to any desired capacity stop, such as 39, 49 or II, indicated on the dial of valve I8A as 2, 3, 4. While we have indicated in Fig. 3that the valves" IIA and ISA are separate, it is equally feasible th'at'they be combined into a single operable mechanism.

We providea pressure reducing valve 59A in the air pipe leading to the transfer valve IIA as we have found it desirable to actuate the piston 6 with" air at approximately 20 p. s. i. pressure, while the air availableto hold the plungers' 44 extended should perhaps be at p: s. i. pressure. I

The proper sequence'of operation of this. syst'em'is'as'followsz 1. Turnthe knob 55 to freset position. This retracts the orifice plate to its maximum opening position in the bore 2.

2. Turn the knob 52 to the capacity stop desired, i. e., 1, 2, 3, or 4. This pushes out the corresponding stop pin so as to engage the shoulder 42 of the piston rod 1 when the orifice plate 4 is lowered into the body.

3. Turn the knob 55 to operate position. This lowers the orifice plate 4 to the desired position and engages the shoulder 42 of the pison rod 1 with the extended stop pin previously selected.

This entire cycle of operation normally takes not more than six to twelve seconds, depending upon the relative position of the stop selected, the existing position of the orifice plate and the size of the orifice.

The lowest stop 38 is not air operated but is fixed in position. When the knob 52 is turned to this designation (1) all shutoff valves 58 are closed so that no stop pins are extended towardthe piston rod. When the knob 55 is turned to the operate position the orifice plat-e moves down until the shoulder 42 engages the fixed stop. Thus the sequence of operation is precisely the same as outlined above regardless of the fact that the lowest or fixed stop is not air operated.

In Fig. 6- we have shown a diagrammatic layout of the pneumatic control system of Fig. 3 with the various piping connections to the transfer valve and selector valve. Through the agency of the knob 55 of the transver valve HA the piston rod and orifice plate are retracted to their uppermost position (on the drawing) and then the selector knob 52 is turned to the numeral designating the selected orifice capacity (travel stop). By turning the knob 52 the cams connected thereto actuate the shutoff valves, as clearly shown in Fig. 6, so that the selected stop is extended into the path of the shoulder 42 of the piston rod and held in i:

that position. The transfer valve HA is then turned to the operate position which moves the piston, piston rod and orifice plate downwardly until the shoulder 42 on the piston rod engages the selected stop. Thereafter air pressure on the top of the piston holds the should-er 42 firmly against the selected stop until it may be desired to make a further change.

It will be seen that when the knob 52 is turned in the proper direction the cam 56 is rotated in a rising direction, and when the selected notch of the wheel 51 is reached the cam 56 corresponding thereto has reached its highest position of rise and has lifted and opened the shutoff valve 58.

This allows high pressure air from the supply pipe 59 to be admitted to the pipe 56 and act upon the bellows 45 of the stop to extend the plunger 44 into the path of the shoulder 42. The mere fact that certain other of the valves may be opened through cam action while the knob 52 is being turned harms nothing because even though various other stops are successively extended into the path of the shoulder 42, they will be individually retracted by the action of their individual springs 46 as soon as the respective cam has passed beyond its highest point and the respective valve 58 has returned to closed position.

It will be apparent that when the valve 58 has again seated and has shut ofi the supply of air from the pipe 59 to the pipe 60 then full air pressure is trapped within the pipe 60 and the bellows 45 so that the stop pin 44 would stay in its extended position although it were desired that the spring 46 retract it out of theway of the shoulder 42. To prevent this we have provided. that sufiicient clearance is allowed around the valve stems 6! so that there is a continuous minute bleed to the atmosphere regardless of the position of the valve 58. Thus there is a minute bleed even when the valve 58 is open and full line pressure is applied to the pipe 66. This bleed, with the valve 58 closed, allows a relief of the pipe 60 so that the spring 46 will retract the plunger 44 in sufficient time to have it out of the way of movement of piston rod 1 and its shoulder 42.

In Fig. 7 we show a diagrammatic layout of a pneumatic control system similar to that of Fig. 6 but having a great-er number of stops in connection with an adjustable orifice. For example, when the desired number of stops is greater than a certain number it is extremely diflicult or impossible to include them all physically in a single selector valve. Beyond this number two or more selector valves may be used and then it becomes necessary to properly interlock the transfer valves and the various selector valves so that the proper preselected stop is the only one which is extended to limit or control the position of the orifice plate, and furthermore that none of the stops may b extended into the path of motion of the shoulder 42 to interfere with travel of the piston rod and orifice plate on its way to the selected position.

The individual position selectors are similar to the position selector valve of Fig. 6. In addition, however, a shutoff valve is incorporated in the circuit of the interlock mechanism in each selector valve to make it impossible to operate either position selector until the other selector is in the ofi position. This is accomplished as follows:

Suppose that one of the positions included in selector valve 6| is to be used. Air cannot pass through the interlock valve 62 in the selector valve 63 until the selector knob 64 is in a predetermined position. When this knob is so positioned then the air passes through the interlock valve 62 and to the bellows of the interlock mechanism 65. This releases the motion of the cam shaft of the system 6| and permits the knob 66 to be turned A to the desired stop designation when the orifice plate is fully retracted.

This system is interlocked with the position of the adjustable orifice itself exactly as previously explained, referring to the interlock 53, so as to make it impossible to turn either of the selector knobs 64 or 66 until the orifice is fully retracted. The only difference in sequence of operation of this system as compared to the one shown on Fig. 6 is the settingof the knob 64 or 66, which is not being used, to the ofi position.

In sequence it is first advisable to turn the transfer knob 55 to the reset position, then turn the knob 64 or 66 which is not to be used to the off position, and then turn the other knob either 66 or 64 to the indicated stop position desired. Thereafter to return the knob 55 to the operate position.

In general, we have provided an adjustable orifice adaptable to remote positioning, so that an operator at a remote point may select the orifice capacity or orifice position which he desires to utilize in the measurement of a flowing fluid and accomplish a positioning of the orifice plate to the selected position swiftly and accurately without the necessity of interfering with'the fiow of the fiuid in any respect.

It is apparent that it is not necessary that this system be pneumatically actuated, but it might equally as well be a hydraulic system utilizing oil or other fluid as may be desired. Such particular details'or changes in the mechanism to adaptthe What we claim as new, and desire to secure by Letters Patent .of the United States, is:

.1. The combination with an'adjustable orifice ing thereby .a pressure diiferential bearing a knownsrelation to rate ioffluid flow, of a fluid .pressure-powermeans arranged to move said ole-- mentbetween extreme limits, and fluid pressure operatedmeans engageable by said power means and providing a plurality of positionable intermediate travel limits for said power means.

2. The combination of claim 1 including manually operable means for selecting the intermediate travel limit and controlling the flow of pressure fluid to said fluid pressure operated means for limiting the travel of said power means and the amount of restriction to fluid flow to be exerted by said element.

3. The combination of claim 1 wherein the means providing a plurality of positionable intermediate travel limits for said power means comprises a member having a plurality of lands engageable with said power means for limiting the travel of the power means in one direction.

4. The combination of claim 1 wherein the means providing a plurality of positionable intermediate travel limits for said power means comprises a series of extendible-retractible stops movable selectively into the path of said power means for limiting the travel of the power means in one direction.

5. The combination of claim 1 wherein the positionable intermediate travel limits of said power means comprises a member having a plurality of lands engageable with said power means for limiting the travel of the power means in one direction, and means for remotely selectively moving said member until a desired land is in the path of the power means.

6. The combination of claim 1 wherein the means providing a plurality of positionable intermediate travel limits for said power means com- F5} prises a. series of extendible-retractible stops movable by pressure fluid into the path of said power means for limiting the travel of the power means in one direction, and means including remotely located manually actuated means for supplying [50] pressure fluid selectively to said stops and positioning a desired one of said stops in the path of the power means.

'7. The combination with an adjustable orifice system having a flow restricting element adapted '55] for movement relative to a flowing fluid for creating thereby a pressure differential bearing a known relation to rate of fluid flow, and power means arranged to position said element between extreme limits, of a member adjacent the travel 60 path of said power means and having a plurality of lands thereon each providing a limit to travel of said power means in one direction, and separate power means for positioning said member to bring a preselected land into operative relation 5 with the first power means.

8. The combination of claim 7 including manually actuated remote means for selecting the desired limit of travel of said first power means and for then controlling the separate power means to position said member.

9. The combination of claim 7 wherein the separate power means for positioning the member is a fluid pressure actuated power means, and

'10 for establishing @afluid loading pressure corresponding to the desired travel limit for theelementand applying said loadingpressure to said separate power means.

10. The combination of claim 7 wherein the separate power means for positioning the memher is aafluidzpressureactuated power means, and manually:actuatedselector means is provided for selecting the desired limit of travel of said first power means and for then controlling the separate power means to position said member, and manually actuated means is also provided for controlling the movement of the first power means toward and away from the member.

11. The combination with an adjustable orifice system having a flow restricting element positionable transversely across a flowing fluid for creating thereacross a pressure differential bearing a known relation to rate of fluid flow, of a pneumatic power piston connected to position said element between extreme limits of travel, the improvement therewith of means providing intermediate limits of travel for the element, pneumatic means for making eifective a selected one of the intermediate travel limits, and means for supplying pressure fluid to said power piston for moving it in one direction until it reaches said selected limit.

1.2. The combination with an adjustable orifice system having a flow restricting element positionable across a fluid flow path for creating a pressure differential bearing a known relation to rate of fluid flow, of a pneumatic power piston connected to position said element between extreme limits of travel, a member having a plurality of lands each providing an intermediate travel limit for said piston and element, means for supplying air under pressure to said piston, remote manually actuated valve means for controlling said air supply means to efiect movement second pneumatic power piston connected to position said member to bring a selected travel limit land into engageable relation With said first piston, means for supplying air under pressure to said second piston, and remote manually actuated valve means for controlling said last mentioned air supply means.

13. The combination with an adjustable orifice system having a flow restricting element positionable across a fluid flow path for creating a pressure difierential bearing a known relation to rate of fluid flow, of a pneumatic power piston connected to position said element between extreme limits of travel, a plurality of eXtendible-retractable means each providing when extended an intermediate travel limit for said piston and element, means for supplying air under pressure to said piston, remote manually actuated valve means for controlling said air supply means to effect movement of said piston relative to said limits of travel, and means including remote manually actuated selector means for selecting a desired intermediate travel limit and thereafter causing the corresponding one of the extendibleretractable means to be extended and limit the travel of the piston and element.

14. The combination of claim 13 wherein the extendible-retractable means are fluid actuated, and the means including the selector means also including means for supplying pressure fluid to said extendible-retractable means, and valve means for directing flow selectively to said exa manually actuated selector means is provided tendible-retractable means for extending the REFERENCES CITED The following references are of record in the file of this patent:

Number 12 UNITED STATES PATENTS Name Date Fisher Dec. 10, 1918 Roucka Apr. 13, 1926 Rouck'aua Apr. 13, 1926 Wehling Apr. 15, 1930 Jacoby et a1 Sept. 29, 1936 Saur Feb. 6, 1940 Norman et a1. Mar. 5, 1940 Berard Sept. 3, 1940 McCullough May 18, 1943 

